Balanced fuel injection pump



July 15, 1969 F. aoRowlEc ETAIT BALANCED FUEL INJECTION PUMP Filed Feb.28, '1968 5 sheets-sneu 1 EY JQ.

F. BOROWIEC ETAI- BALANCED FUEL INJECTION PUMP July 1s, 1.969

5 Sheecs-Sheecl 2 Filed Feb. 28, 1968 m W m c c M\w.\\\\,\\1\\\\\\ .1 4F E E mfw. @www July 15, 1969 F. BoRowlEc ETAI- 3,455,245

BALANCED FUEL INJECTION PUMP Filed Feb. 28, 1968 5 sheets-sheet s FLE-E-37 30/ INVEITJTORS Fraz-1.1i E: :lrcnw l; c'

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July l5, 1969 F, BoRowlEc ETAL 3,455,246

BALANCED FUEL INJECTION PUMP Filed Feb. 28. 1968 5 Sheets-Sheet 5 WwMNum Il.

Il Il llll Il I NVENTORS United States Patent O 3,455,246 BALANCED FUELINJECTION PUMP Frank Borowiec, 213 School St., Chicopee, Mass. 01013 andStanley Borowiec, Cedar St., Three Rivers, Mass. 01080 Filed Feb. 28,1968, Ser. No. 709,047 Int. Cl. F04b 13/02, 19/22 U.S. Cl. 103-2 10Claims ABSTRACT F THE DISCLOSURE The within invention is concerned withfuel injection pumping mechanisms. In the particular embodiment hereindescribed, a rotating shaft has connected to it a plunger assembly. Theplunger assembly rotates. At the bottom of the plunger assembly are fourrollers or at |wheels which, as the plunger assembly rotates over thecam surfaces, will roll and will cause the plunger assembly to go upagainst the tension of a return spring dependingupon whether they go upon the surface or down on the surface of the cam. The surfaces which areemployed are those of cams. The shape of the cams have beenpredetermined and predesigned and cause the plunger assembly to go upand down at predetermined times. The movement of the plunger assembly,up and down, controls the inlet and outlet of oil into the combustionchamber under the further control of a unique and novel governor. Whenthe plunger assembly is in an upward position, it forces oil to enterinto an upward chamber causing pressure on a metering piston which inturn forces a greater pressure on a previously pressurized governorchamber, forcing oil out at a particular predetermined pressure. vWhenthe oil is forced out of the governo-r chamber, it relieves itself byforcing oil from the high pressure chamber of the plunger into thegovernor low pressure chamber. The governor chamber, therefore, releasesitself by forcing its valves, `which are under spring tension, outwardlycontrolling the ow of oil to the combustion chamber in a balancedaction. Prior to the pressure being applied in the governor cham-ber,there is a relieving effect from the piston chamber and fuel is ejectedto the combustion chamber inlet. This operation is a continuous cycleand controls the amount of fuel entering the combustion chamber for theenergizing of motors and the like. The effect of injecting the fuel tothe combustion chamber is continuous and creates a more efficient andsmoother ope-ration of the engine. When the plunger applies pressure onthe return spring,` the rollers are applying downward pressure into thesupply chamber causing oil to flow therefrom in the system, to beapplied to the system.

This invention is concerned with fuel injecting pumping systems andparticularly with a fuel injection system that improves upon the jerkeffec of prior fuel injection pumps and systems.

Particularly in the diesel engine -which burns oil for its fuel,injection pumping a-rrangements have been devised for delivering thefuel oil to the combustion chamber in order to obtain a strong, quickstroke of the engine. It is desirable at slower speeds in a fuelinjection diesel-type of engine to have the stroke smoother and longerin order to obtain the greatest amount of torque displacement in thechamber.

It is, therefore, a principal object of the within invention to providea fuel injection pumping arrangement that will deliver fuel oil to acombustion chamber continuously, without jerking, under constantpressure, and without vacuum or air entering into the feed lines.

It is still another object of the within invention to provide a novel'balancing arrangement operated by a plunger in conjunction with aspecially designed cam.

3,455,246 Patented July 15, 1969 'ice It is yet a further object of thewithin invention to provide a fuel injection pumping arrangement whereinthe camming action operates on a fixed axis so that the plungeroscillates back and forth as rollers from the plunger assembly move overthe cams.

It is an additional object of the within invention to provide a fuelinjection pumping arrangement that is balanced so that a governor undercontrol of a plunger means controls, in an even amount, the tiow of oilthrough the outlet from the pumping system to the inlet of the workload.

It is another object of the within invention to provide a cammingarrangement for controlling the operation of a fuel injection pumpingsystem wherein the camming arrangement may be determined as a functionof the revolutions per minute.

It is yet a further object of the within invention to pro vide agovernor that may be pre-set and produce the same fuel delivery curveregardless of the amount of plunger leakage.

It is an additional object of the within invention to provide a fuelinjection pumping arrangement that is balanced and controlled so that aneven fi-ow of fuel is sent to the work load by means of a completelymechanical system.

It is still a further object of the within invention to provide a fuelinjection pumping system that is inexpensive in the cost of manufactureand performs all of the objects aforementioned.

yIt is yet a further object of the within invention to combine theprinciples of a common rail and jerk type fuel injection pump.

This new innovation has improved features such as: (a) continuallypressurized injection lines, (b) automatic relief so that if aninjection nozzle becomes plugged, it will not damage the plunger, and(c) the pressurization of the plunger head at all times will preventformation of vacuum and bubbles.

With positive pressurization of injection lines, the fol-v lowingadvantages exist: (1) eliminationof destructive cavitation and erosion,(2) no vaporization of the oil in the injection lines so that there is agovernable straight line curve over a much higher r.p.m. range, and (3)a much smaller required working load over the plunger.

These and other objects a-re obtained by the arrangement wherein arotating shaft operates a plunger system Within the center of the fuelpump. Mounted at the lower portion of the plunger arrangement arerollers. The rollers are mounted in such a way that when the plunger isrotating, the rollers are caused to roll over the surface of whateverlwith which they are in contact. In this instance, specially predesignedcams are located beneath the rollers. The cams are mounted on a fixedaxis and oscillate back and forth. The shape of the cam determines theamount of motion of the plunger up and down against its spring action.Each of the several rollers operates first over one cam and thenv overanother. There are a similar number of cams as there are rollers. Theoperation of the rollers over the cams determines the oscillation of theplunger arrangement up and down causing the control of pressure into aplunger chamber which in turn causes pressure into a governor chamber,as well as a supply chamber beneath the cams.

The change of pressure in the various chambers causes a balance anddetermines the amount of the liow of oil from the reservoir outlet tothe combustion chamber of an engine or to the work load, as the case maybe.

For a better understanding of this invention, reference is made to thefollowing detailed description and specification and to the drawings inwhich:

FIGURE 1 is a diagrammatic cross-section view in elevation of the entirefuel injection pumping system.`

FIGURE 2 is a side elevational, diagrammatic view of the rollers passingover the oscillating cams.

FIGURE 3 is a cross-sectional View taken along line 3-3 of the view ofFIGURE 1, looking down onto the pump system as shown in FIGURE 1.

FIGURE 4 is a side perspective view of the control bar 14.

FIGURE 5 is a cross-sectional View taken along lines 5-5 of FIGURE 1looking down on that portion of FIG- URE 1.

FIGURE 6 is a top plan View in diagrammatic form of the cam support discassembly.

FIGURE 7 is a side perspective View of the supply pump disc upon whichthe cams are mounted.

FIGURE 8 is a side elevational perspective view of the upper portion ofthe plunger assembly showing the opening for permitting oil to passtherethrough.

FIGURE 9 is a view in cross section along lines 9-9 of the View ofFIGURE 8.

FIGURE 10 is a top plan view of the disc assembly 42 showing theopenings wherein the cams are mounted.

FIGURE 11 is a cross-section view taken along line 11-11 of FIGURE 1showing the area proximate the metering plunger assembly.

FIGURE 12 is an elevational perspective view of the plunger assemblyshowing the mounting of the rollers upon the lower portion thereof.

FIGURE 13 is a diagrammatic elevational View of the governor assemblychamber.

FIGURE 14 is a side elevational perspective view of the metering pistonassembly.

FIGURE 15 is a side elevational diagrammatic view of the plunger headassembly.

FIGURE 16 is a side elevational perspective view of the cylinder mainhousing.

FIGURE 17 is a side elevational diagrammatic view of the cam mountingassembly.

FIGURE 18 is a portion in perspective elevation of the metering piston.

FIGURE 19 is a diagrammatic cross-section View of the pumping systemshowing the roller at a particular point on 'the cam wherein all of thereservoirs are being filled with oil.

FIGURE 20 is a diagrammatic cross-section view of the fuel injectionsystem showing the roller at a second position on the cam wherein allreservoirs are commencing the act of becoming pressurized with oil.

FIGURE 21 is a diagrammatic cross-section view of the fuel injectionsystem showing the roller at a second position on the cam wherein thefuel has been injected into the chambers and the relief of each of thechambers is in operation.

A drive shaft 1 is cylindrical in shape and is connected in aconventional transmission arrangement to a take-olf gear from the motoror other energizing source. The drive shaft 1 has a spline section 23.The teeth of the spline section 23 are in engagement with the teeth inthe conventional manner with the injection plunger 5. This can be seenin the View of FIGURE 1. The injection plunger 5 has a long narrowportion extending upwardly and then extends out to a main body portionwhich surrounds the shaft 1. Reference is made to the view of FIGURE 12wherein the injection plunger 5 can be seen in detail. In the main bodyportion of plunger 5, there is connected on the lower surface thereofthe cam roller lugs 33. The lugs 33 have bifurcated protrusions in whichare mounted the roller 2 by means of the pin 32. In the embodimentshown, there are four separate roller assemblies.

The bottom lines in FIGURE 12 are indicated by the numeral 25 which maybe referred to as the spline opening or hole. This is in location wherethe spline teeth engage the teeth 23a of the shaft 1.

At the upper portion of the plunger 5 is located the opening 55 whichmay be referred to as the injection plunger fuel hole 55. An elongatedfuel opening 56 appears in the View of FIGURE l2 on the left side of theplunger 5. Within this area 56 is the fuel connecting hole 57. On theopposite side of the plunger 5 is a milled out section 41.

Beneath the plunger assembly 5 in the view of FIG- URE 12 and as shownin the view of FIGURE l, is the cam assembly.

In addition to the View of FIGURE l, reference may be made to the viewof FIGURE 17 and the View of FIGURE 10, FIGURE 6, and FIGURE 7 tounderstand how the cams are mounted. Movement of the cams can be seen inthe view of FIGURE 2 in conjunction with the rollers.

The cams 3 are mounted by the cam pivot pins 29 which are verticallymounted. Within the cam support disc 42 within the cam lugs 31 are thepin openings 53. The pins 52 pass through openings in the cams 3 andthrough the pin 4openings 53 in the lugs 31 for vertically mounting thecams. The cams will move back and forth on the pins 52. However, it isnecessary that the cams move back and forth within limitation and a camsupporting disc 42 is located above the disc 4, upon which lugs 31 aremounted for controlling the motion of the cams 3 on the pins 52, as wellas preventing the cams 3 from p lateral movement.

The disc 42 can be seen in a top plan view of FIGURE 10. There is acenter opening 44 for the shaft 1 in the center of the disc 42. Thereare four slots 43 located in quadrants opposite the center disc 44. Theslots 43 permit the cams 3 to pass therethrough and are sucientlydesigned to permit the cams 3 to move back and forth Within the slots43. It is to be noted that these are elongated slots and are so designedas to prevent the cams 3 from lateral movement. The cams 3 pivot as canbe seen in FIGURE 2 on the axis of the opening 30. The opening 30permits the pin 29 to pass therethrough to make the cams engage with thedisc guard 42. The dotted lines 30 in FIGURE 10 indicate the openings.The pin 29 can be seen in the view of FIGURE 1. It can also be seen inthe view of FIGURE 6. Beneath the disc 4 is a seal or grommet disc 39 tomaintain a pressure tight cavity.

In FIGURE 1 located above the plunger 5 is the metering and reliefpiston 6. The cross-section diagrammatic view of the area about therelief piston 6 can be seen in the view of FIGURE 11. The cylindricalshaped pump head 18 has a small circular cut 50 located around theperiphery of the cylindrical shape metering and relief piston 6. Acrossthe top of the piston 6 is the fuel elongated opening 48.

Within the opening 48 and in the center of the metering and reliefpiston 6 is a fuel aperture or hole 47.

The view of FIGURE 5 is a cross-sectional View taken along line 5 5 ofFIGURE 1 looking down on that portion of FIGURE l. The pump head 18 iscircular in crosssection and has protruding at its four quadrants asupply head lug which have within each a bolt hole 37.

The top of the plunger 5 can be seen in the center of the pump head 18.It is located within a milled out section 41. The injection plunger fuelhole is located within the center of the plunger 5. Connected to thefuel hole 55 is the elongated fuel opening 56 which is connected to theinjection lines 76 which are tubular and made of steel to withstand highpressure. Since the plunger 5 rotates, it can be seen that the effect islike a railroad turn-table in that the elongated fuel openings 56 willmate with the various openings opposite the injection lines 76 asplunger 5 rotates about its vertical axis. There are dotted lines 49beneath the cross-section in the View of FIGURE 5. The dotted lines 49indicate the disc-shaped circular member surrounding the periphery ofthe plunger 5. This can be seen in the view of FIGURE 1 andV is arecessed cut in the pump head 18. The inlet tubular assembly 79connected from the supply pump cavity or chamber 34 can be seen indotted lines in the View of FIGURE 5, as well as midway in the headassembly in the view of FIGURE 1.

The view of FIGURE 8 shows, in side-elevational perspective, thearrangement of the milled out section 41 of the plunger 5, as well asthe elongated fuel opening 56 and the fuel connecting hole 57, all asdescribed in the view of FIGURE 5 previously. The injection plunger fuelhole 55 can -be seen in the elevational view of FIGURE 8. FIGURE 9 alsodiscloses this in an exploded arrangement. However, the view of FIGURE 9is a top elevational view.

The supply pump inlet check valve asembly which is located at the bottomportion of FIGURE 1 is designated by the numerals 7, 7a and 7b. Thevalve consists of a housing 7 in which is mounted a spring 7a andproximate the spring 7a is a solid ball 7b. The presure of oil appliedagainst the ball 7b will push or compress the spring 7a permitting oilto ow therearound into the chamber 34. The chamber 34 is hereinafterdesignated as the supply pump fuel area 34. Similarly, on the left handside of the View of FIGURE 1 is an outlet check valve assembly similarto the inlet check valve assembly designated as 7, 7a and 7b. Thissystem is designated as 8, 8a and 8b and similarly operates when the oilpressure against the ball causes the spring to close. In this instancethe ball 8b exerts a pressure on the spring 8a.

The flow regulating valve assembly 9 may be seen in the view of FIGURE 1and is located near the right hand corner of the view. The ow regulatingvalve assembly comprises the Valve head 9, the spring attached thereto9b, and a housing 9a. Again the oil in the direction of the arrow willexert pressure againt the head 9 of the valve and compress the spring 9bwithin the housing 9a.

Reference is made to the view of FIGURE 3 wherein is located the lowidle governor control valve 10. The valve 10 is similar in many respectsto a piston. It has connected to it the spring 10a and a bolt 26.

There is also located in the View of FIGURE 3, the full load governorcontrol valve assembly 11 which is similar to the style of the valve 10having its own spring 11a connected to a bolt 51. The tubular controlvalve ducts 77 connect with the valves 10 and 11 respectively. Thearrangement of the ducts 77 can be seen clearly in the cross-sectionaldiagrammatic view of FIGURE 3. The ducts 77 connect to the hole 28, andthe low idle and full load control bar 14. The governor ball check valve13 has a spring 13a connected within the ducts 77. The governor housingfuel reservoir 21 which is cylindrical in shape, is connected to thegovernor ball check valve 13 via the duct 77. The metering and reliefpiston fuel hole 54 is located within the reservoir 21 and can be seenin FIGURE 3. There is located on the bar 14, a control bar regulatorwhich has a flat section 45 as well as a control bar regulator pin 46.There is also within the bar 14, a hole 27. Hole 27 is located in thearea of the upper portion of the ducts 77 when the bar drops downwardlyas shown in the view of FIGURE 3 is dotted lines. The bar 14 has twopositions as shown by the dotted line area permitting the openings at 27and 28 to pass or go through into the ducts 77 through the valveassemblies 10 and 11 respectively. At the bottom of the valve 11 is bolt51'. The bar 14 can be seen in a side elevational view in FIGURE 4.

In FIG. 13 is located a diagrammatic elevational view of the governorassembly chamber 16 with the governor housing fuel reservoir covers 60on top of the chamber 16. Clearance hole 65 is for the metering andrelief piston 6. There are threads 61 located on the interior surface of16. The threads 61 can be seen clearly in the view of FIG URE 1. Theinlet 5 in housing 66 is connected to the side walls of the chamber 16.The governor control hous ing 75 is mounted to the right upper portionof the chamber 16.

FIGURE is a side elevational diagrammatic View of the assembly of pumphead 18. There is a cut out area of 64 atop of the pump head 18. Thereis a threaded area 63 on the outer surface of 18. The threads 63 areopposite the threads 61 in FIGURE 1. There is a small circular cut 50located in the pump head 18. This can be seen in the view of FIGURE 1.There is a large circular cut 49 also located in 18 and this can be seenin the View of FIGURE 1. At the lower portion of the pump head 18 arethe head lugs 35 in which are located the lug bolt holes 37. At thelower portion of the pump head 18 is the groove disc 70. The ring seal20 ts within the groove 70 and can be seen in the View of FIGURE 1.Injection plunger hole 71 may be seen in dotted lines in the view ofFIGURE l5 located within the pump head 18.

The view of 16 is a side elevational perspective view of the cylindermain housing. This is referred to as the pump housing 19. The bottom ofthe pump housing 19 is the pump housing flange 59. The threaded holes 68for supply pump outlet check valve 8 are located Within the pump housing19. There are also threaded openings 67 within the surface of 19 forengagement with the threaded surfaces of 7. The hole 67 for the shaft 1is located at the bottom of the pump housing 19.

In the view of FIGURE 1 the governor sump inlet valve 12 can be seen onthe left side thereof. The valve 12 comprises a spring 12a within thetubular inlet valve housing 66.

A shut-olf valve 15 may be seen in the view of FIG- URE 1. This may becontrolled manually.

A spacer 17 is located between the pump head 18and the governor housing16. The purpose of 17 is in the nature of keeping proper sealing andspacing between the various component parts between which it is located.

In the view of FIGURE 1 above the plunger 5 may be seen the fuelcompression area 22.

Surrounding the plunger 5 above the housing that supports the rollers 2is located a compression spring 24. This maintains the rollers incontact with the cam surfaces because of its tension.

In the view of FIGURE 1 are located bolts 36 which engage the pump head18 with the pump housing 19. In the Ibottom of the governor housing fuelreservoir 21 isl located a ber disc 38 for sealing and maintaining thereservoir pressure in 21.

In the view of FIGURE 14 there is shown the perspective elevational viewof the metering and relief piston 6. As stated, atop piston y6 is thefiber disc 38 which has already been referred to as being in the bottomof the governor reservoir 21. Beneath 38 on the lower sidel thereof isthe relief piston plate 62.

The spill tube or fuel return 72 can be seen in the view of FIGURE 1connected to the supply pump sucti'on tube 74. The governor and head lltube 73 is conn ected to the head fill tubular duct 79 which isconnec'ted to the injection plunger fuel hole 55. The fill tube 73 isalso connected to the valve assembly 8, and also connected to the inletvalve housing 66 and the governor sump inlet valve 12. The spill valveduct 78 is connected to the spill tube or fuel return 72 and also to thevalve 15. The reamed cylinder hole 80 is located within the duct 77before the valves 10 and 11. (See FIGURE 3.)

The system herein described is pre-pressurized. That is to say that allof the tubes, ducts and chambers have been filled with oil and placedunder a pressure of approximately fifty pounds per square inch. All ofthe tubes, ducts and chambers have thus been made of a sufficientlystrong material to withstand this pressure. In the event that thepressure is reduced by leakage, the system will of course not workproperly unless it is preprimed with pressure. All leaks, however, mustbe corrected and closed in order to insure proper and efficientoperation, in such a case.

As to the details of operation, reference should be made not only toFIGURE 1, but to the views of FIG- URES 19, 20 and 21. As in mostengines, it is necessary to turn on the energizing source which may beeither from" a battery or from a source of electricity which turns overthe motor. Once the engine starts, shaft 1 which is connected to thetransmission system of the engine (not shown) starts to rotatecounter-clockwise, the rollers 2 at the bottom of the plunger assemblyof FIGURE 12 roll over the surfaces of the cams 3. Reference at thispoint of the detailed description of the operation should be had toFIGURES 19, 20, and 21. It can be seen in each of these figures that therollers 2 roll over the surfaces of the cams 3 in an up and down manneras shown by the shape of cams 3 in the aforesaid views of FIGURES 19,20, and 21. The rotation of the rollers causes the plunger 5 and itsassembly to go up and down within its housing 18. The up and down motionof '5 controls the operation of the fuel within the system. For example,in the view of FIGURE 19, when the roller 2 is near the bottom of thecam 3, the plunger within the chamber 18 is at a low point. The fuelfrom the duct 73 flows into the fuel compression area 22. As the rollers2 move up on the cam 3 as shown in FIGURE 20 they cause a compression tobuild up in the area at 22. When the rollers 2 reach the point at thetop of the cam 3, in the view of FIGURE 21, a complete pressure is builtup in the area 22 by the applied pressure from the top of the plunger 5.This pressure in 22 now causes oil to go out through the opening 76 fordelivery into the load or compression cylinder of the engine. Actually,the delivery of the oil to the load takes place when the roller 2 is notquite at the point shown in the view of FIGURE 21 on the cam 3. When theroller 2 reaches the point shown on the view in FIGURE 21 on cam 3, thepressure is of such magnitude in the chamber 22 that it forces themetering and relief piston `6 to be forced up into the chamber 21. Theoil from the chamber 21 is then under an increased pressure and causesrelease of the valve 13. The oil now passes out of valve 13 from thechamber 21 l(see FIGURE 3) down through duct 77 through the opening 28in the control bar 14, through duct 77 within the governor housing 16,through valve 11, and into duct 77 as shown located on the other side ofvalve 11 in the housing 16. The excess is then caused to flow into duct72 (see FIGURE 21) and returns to the sump area at 34 to be pumped over.

Going back to FIGURE 19, at the time the roller 2 started to move up thecam surface 3, a vacuum was created in the reservoir 34. This causes oilto come from a source into the reservoir 34 through the duct 74. As thefuel oil fills up the chamber 34 from the source through the duct 74,the vacuum is now eliminated and as the roller 2 starts to go up thesurface of the cam 3 as shown in FIGURE 20, there is pressure exertedupon the cam 3 by the roller 2 causing the plate 4 to exert a downwardpressure against the top of the area at the reservoir 34 causing presureto be placed upon the oil Within 34 against the valve 8. This causes aflow of oil through the valve 8, through duct 73, up into the inlet 79.At the same time, oil is caused to flow from the reservoir 34 up theduct 73 on the left side of the view of FIGURE 20, through the valve 12into the governor reservoir 21, maintaining a constant amount of oil inchamber 21. This action maintains an equilibrium or balance with the oilin chamber 34 and the oil in chamber 21. It is obvious that as roller 2rolls up the surface of cam 3 as shown in FIGURE 2l, the maximum amountof pressure on plate 4 against the reservoir 34 in its compressedposition will cause the last flow of oil in the duct 73 in bothdirections up to valve 12 and up to the inlet 79.

The cycle is now complete and the roller 2 starts out again on the nextcam 3 to perform the same function. It is to be noted that there arefour rollers 2 and four cams 3 and that the complete rotation of theshaft 1 causes each of the four rollers `to roll over each of the fourcams. Note the four cams are located in the quadrants of thecross-section in FIGURES 6 and 10.

`Of importance in the detail of operation is the milled out section 41and the plunger 5.

In the View of FIGURE 19, the outlet 56 is not in proper position topermit oil to liow through to 76 from the inlet at 79. However, in theView of FIGURE 20 when the roller is part way up the cam surface 3, theinlet 73 is now in a liquid engagement with the outlet 76 on the righthand side of the view of FIGURE 20. This can be seen more clearly in theview of FIGURE 5. This is the turntable effect talked about previouslyin the specification. As the shaft 5 rotates counter-clockwise, there isan opening at 55 connected to the duct at 57. The duct at 57 first makesliquid contact with 56, then as shaft 5 rotates, it closes olf contactwith 56 and picks up liquid contact again with the vertical entrance of76 in the bottom quadrant. The plunger 5 then continues to rotatecounter-v clockwise so that it picks up contact with the duct at 76 inthe right hand quadrant, and so on to the upper quadrant and back to itsoriginal position. Oil is permitted to flow for that moment when 57 isin contact with 56 or 76 as the case may be in each quadrant. (SeeFIGURE 5 to understand the turntable effect.)

One of the important effects of this turntable arrangement is to preventany vacuum being created in the chamber 22. This eliminates vaporbubbles and maintains a much evener ow of oil to the engine.

The clearance `41 of the plunger 5, FIGURE 5, is feeding oil to theremaining duct outlets 76 when there is liquid contact with the outlet76 in the quadrant in which the elongated fuel opening 56 is engaged.When 56 is not in engagement with a duct 76, there is oil being fed from41 to all ducts 76. The elongated fuel opening 56 is like' a jet gun.The effect of 56 rotating into the ducts 76 in each quadrant is like apulsing jet, shooting oil under 4,000 pounds per square inch pressureinto the injection nozzles, not shown, of the engine. The speed ofrotation of the plunger 5 is the same speed of rotation of the fuelopening 56, obviously, and therefore, increased speed of rotation willincrease the delivery of oil from 56.

The oil feeding from 41 is to soften the recoil effect of the oiljetting from 56 when 56 is in liquid contact with 76. Oil feeding from41 to the other ducts 76 keeps them free of air, bubbles, and vapor. Thepressure of oil from 41 is at about 500 pounds per square inch.

The end result of this arrangement is that the same amount of oil thatis injected into the system is ejected, eliminating vacuums and vaporbubbles. The speed of the shaft 1 will operate synchronously with thespeed of the engine. The faster the engine, the faster the rotation ofthe shaft 1 and consequently the plunger 5 will rotate faster. From thisexplanation, this pumping system may work at extremely high speed, muchfaster than heretofore of any known pumping arrangement. The prior artwill not permit the oil to be pumped at high rates of speed becauseflo-w control is ungovernable whereas the within disclosure teaches theidea of a balanced arrangement in the governor chamber at 21 so that atall times there is oil available in a balanced arrangement between theoil in chamber 21 and the oil in chamber 34.

One of the important details of structure that should be emphasized isthe fact that there is a brous dise 39, which is located above the topof the lower chamber and is in contact with the supply pump disc 4. Theiiber disc 39 actually moves up and down within pump housing 19 undercontrol of the pressure exerted by the roller 2 against the cam 3. Thedisplacement of fiber disc 39 ex' pands or contracts the supply pumpfuel chamber 34 causing oil to flow therefrom as previously explained.Since the material of disc 39 is fibrous. It is resilient and oil proofso that no oil can pass above it.

Similarly, in the governor chamber 21 there is a fiber disc 38 at thelower portion thereof in contact with the metering piston 6. As statedwhen the metering piston 6 exerts a pressure on the fiber disc 38, thesize of governor chamber 21 contracts or expands. The amount of pressureexerted on relief piston 6 is dependent upon the position of the roller2 in contact with the cam 3 as already stated. Again because the disc 38is made of fiber material, it is oil proof and resilient and will movewithin the housing 16.

We claim:

1. In a fuel pumping system, a moveable plunger assembly, a housing,said plunger assembly located within said housing, roller means attachedto the botton of said plunger, a plurality of cams moveably mountedbeneath said roller means, spring means for causing said roller means tobe in contact with said cam surfaces, said cam surfaces being of apredetermined shape whereby when said rollers are in contact therewithsaid roller means will move upwardly and then downwardly upon same assaid plunger assembly rotates within said housing, a chamber containingoil mounted beneath said cams, a governor chamber containing oil mountedabove said plunger assembly, outlet means in both of said upper andlower chambers for releasing oil therefrom when pressure is appliedagainst said chambers, a transmission system having a drive shaftconnected to said plunger assembly for rotating said plunger assembly,said plunger assembly having means thereon for causing pressure againstsaid upper chamber when said roller means are on the upper portion ofthe cam surfaces and said cams having means thereon for causing pressureagainst the lower chamber when said roller means are on the uppersurfaces of the said cams causing oil to be ejected from each of saidchambers.

2. In a fuel pumping system as described `in claim 1, including a camsupport plate having a plurality of slots therein, said cam supportplate mounted horizontally in said plunger assembly, each of said camsbeing located vertically within said slots, an opening in the center ofsaid cam support plate for enabling the said drive shaft to be connectedto the plunger assembly, said housing including a bottom housing, saidplate being mounted in said pump bottom housing.

3. In a fuel pumping system as described in claim 1, means for releasingsaid oil so as to ow from said governor chamber into said lower chamberwhen said roller means are on the upper portion of the cam surfaces.

4. In a fuel pumping system as described in claim 1, including a pumphead having a plurality of circumferentially spaced openings locatedbetween the plunger assembly and the governor chamber, an injectionplunger located within said pump head, an L-shaped opening within theinjection plunger whereby when said injection plunger is rotating theL-shaped opening will have contact intermittently with each of saidplurality of openings located in said plunger head.

5. In a fuel pumping system as described in claim 2, including a pumphead located between the plunger assembly and the governor chamber, saidplunger head having a plurality of circumferentially spaced openings, aninjection plunger located within said pump head, an L- shaped openingwithin the injection plunger whereby when said injection plunger isrotating the L-shaped opening will have contact intermittently with eachof lsaid plurality of openings located in said plunger head.

6. In a fuel pumping system as described in claim 3, including a pumphead located between the plunger assembly and the governor chamber, saidplunger head having a plurality of circumferentially spaced openings, aninjection 4plunger located within said pump head, an L-shaped openingwithin the injection plunger whereby when said injection plunger isrotating the L-shaped opening will have contact intermittently with eachof said plurality of openings located in said plunger head.

7. In a fuel pumping system as described in claim 1, including agovernor housing, a control bar located in said housing, a plurality ofcontrol valve ducts located within said governor housing, a pair ofopenings within said control bar, means whereby when said control bar isin one position, one opening is in alignment with one of the aforesaidducts in said governor housing, and means whereby when said control baris in another position, a second opening therein is in alignment with adifferent valve duct of the aforesaid plurality of valve ducts, wherebyoil will ow from said governor chamber through either of said openingsdepending upon the position of the control bar.

8. In a fuel pumping system as described in claim 3, including agovernor housing, a control bar located in said housing, a plurality ofcontrol valve ducts located within said governor housing, a pair ofopenings within said control bar, means whereby when said control bar isin one position, one opening is in alignment with one of the aforesaidducts in said governor housing, and means whereby when said control baris in another position, the second opening therein is in alignment witha different valve duct of the aforesaid plurality of valve ducts,whereby oil will How from said governor chamber through either gf saidopenings depending upon the position of the control 9. In a fuel pumpingsystem as described in claim 4, including a governor housing, a controlba-r located in said housing, a plurality of control valve ducts locatedwithin said housing, a pair of openings within said control bar, meanswhereby when said control bar is in one position, one opening is inalignment with one of the aforesaid ducts in said governor housing, andmeans whereby when said control bar is in another position, a secondopening therein is in alignment with a ditferent valve duct of theaforesaid plurality of valve ducts, whereby oil will flow from saidgovernor chamber through either of said openings depending upon theposition of the control bar.

10. In a fuel pumping system as described in claim 9, wherein the firstof said openings in said control bar permits the flow of oil to a ductconnected to said pump head and the second opening in said control ba-rpermits the flow of oil from said governor chamber to said lower chamberbeneath said cams.

References Cited UNITED STATES PATENTS 2,286,928 6/ 1942 Pipkin 10B-2.12,519,733 8/1950 Beard 103-2.1 2,679,804 6/1954 Bischoff 10S-2.12,746,443 5/ 1956 Meyer 10S-2.1 2,827,852 3/1958 Links 10S-2.1 2,831,4734/1958 Liardet 10S-2.1 3,311,062 3/1967 Knapp et al. 103-2.1

HENRY F. RADUAZO, Primary Examiner US. Cl. X.R.

